Counting device



COUNTING DEVICE 5 SheetsPSheet 2 Filed April 8, 195a 5 Ex wwm M L Vwu mE N9 8 EL T 00 /%?&- -7/// w 4% Nm m in i ,1 4 Q5 1 H o b I ii f 9m ll Q iv cm on 1 {I I Rkx [Ii 4 I Wm Q2 B n \V 3 O m X 3 WWW Nov. 2, 1954 M. A. DEMEULENAERE ETAL COUNTING DEVICE Filed April 8, 1953 5 Sheets-Sheet 4 IN V EN TORI. MARCEL DtMcuLcuA 12E.

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ATTORNEYS Nov. 2, 1954 M. A. DEMEULENAERE ETAL 2,693,317

COUNTING DEVICE 5 Sheets-Sheet 5 Filed April 8, 1953 llllll' l Imm INVHV nczz. DEM 01.:

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ATTORNEYS.

United States Patent COUNTING DEVICE Marcel Antoine Demeulenaere .and Robert New York, N. Y;

Denreulenaere;

This invention pertains to accumulator" mechanisms or counting devices, comprisinga series; of. digital. drums of ascending indicia. order together. with. interlinking mechanisms for appropriately actuating. the: same;

Heretofore accumulators or counters ofithe. general type aforesaid have: comprised. both continuous' and dis continuous. types. In the. continuous; types.:all;.indicating drums advance simultaneously, but not equally. In counters of this type based. on. the decimal system, the successive drums advance proportionally to one-tenth, one-hundredth, one-thousandth, etc.: of. the.first. drum. Such. counters are difficult to read,-. by virtuet'of. their continuousmotion, but the. driving: efiortris very. evenly distributed: between successiveudrums.

The discontinuous types.- of. counters:presently irruse have a. Geneva transmission between the. COllJJlEII'IdIUDJS, each. drum advancing by one unit. for each 1 complete revolution of the precedingdrum; In counters of this typewhen the settingis at. 999999, for example; andsone unitisadded at great :speed; severe :strainsareimparted to the II'EHSIIllSSlOH'tEEthi and..shaft;. Conversely. when one is-added to 999999 at a very.low"speed;...the backlash between gears gives a poor alinementofthedigits;

By: reason oflimitedspace requirements;:.the:carryover gear which bridges two; contiguous TCOUlltGFdlUJIlS, usually has only eight teeth; whereas the counter drums, have forty teeth. When the counter drums are. required to. be extremely small, the. carry-over gears andltheir supporting. shaft become quite-.small'and'. fragile-.2 This remains the case even though instead of 3118/40? ratio: of gear teeth, a ratio of 6/ 20 is employed;

Also the resetting of such-counters presents serious technical difficulties. The Geneva. type of' carry-over gear, prevents simultaneous rotation:of'thecounterzdrums for resetting. Either'the'v carryover; gears have; to be disengaged, whichv makes re-engagement: quite: diificu'lt, or thev counter drums. have to becmade -independent-tof these gears, through positioning. pawls. Although" the latter solution. has proved. most: popular; it. limits: the speed of operation, becausetheinertia-of. the: drums must beovercome by the tensionof the positioning; pawl springs.

The counting; devices of the presentinvention eliminate the disadvantages of the: prior art counters abovereferred to, and. embody the advantages of both. continuous and discontinuous counters;. while eliminating. their: disade vantageous features.

In some counters of the present invention. when: one is addedat great. speed to: 999999, the effort is. no greater than at any other status of operation. of the. counter. Also when one is added at low speed to'999999 with counters ofthe present invention, the alinementof. thedigits re.- mainsprecise at all times, alllbacklash. being tak'emup; Instead of the necessity for employing. gear ratios of 8740 or 6/20 between the carry-over gears and. the counter drums, as in prior constructions, the. presentinvention permitsgear ratios of 6/10'; still; much less space: is taken up by the carry-over gears than by prior' devices. In fact, in certain modifications of. the presentinvention as describedbelow, buttwo teethon the carry-over. gear are required, and these are disposed between and'substantiallywithin the peripheries of adjacent counter drums, thereby minimizing spacerequirements.

With the counters-of the. present. invention,. resetting is..easily accomplishedwithcertain modifications, since the counting; drums may be turnedinreverse; and-.al'l- .to-. gether; In certain modifications-no2inertiaproblems-..are

involved, as the functioning. does: not dependcnssprings nor require springs and as special .precautionsehave been taken. Inother modifications: employingsprings, they operate in. such; manner that. energy is stored in; the spring during nine-tenths of anrevolutionof 21a. lower indicia counter drum, which energy. is automatically released duringthe: remaining one-tenth of. a. revolution .to actuate the next higher indicia drum.-

Referencew-illnow be hadto the accompanying .drawingsfor detailedexplanation ofthe various modifications of counting devices. in accordance. withithis invention.

In the drawings:

Fig. 1 is aside elevation: p artlyin axial section astaken at 1.-1. of .Eig, 2, ,while- Fig.v 2lis an end elevation: taken at 2-2 of Fig. 1., of a. counting-device in accordance. with one modification of the invention.

Fig.- 3: is a sideelevat-ion partially in. axial section. as taken at. 3-.-3 of. Fig. and Fig,, 4 is an endelevation as taken.at.4-4 of.Fig 3.of:.a. second modificationof the invention.

Fig. 5 is-a perspective. view ofloneform. of carry-over element employed inthe. device-.ofFigs. 3 and 4;

Fig. 6 is. atop plan viewof such a carry-over element;

Fig. 7.is;an axialasectional.elevation as taken at 7-7 of-Fig;. 8, and Fig; 8. issan end elevation. as taken at 8-8 of Fig. 7, of. still a further'modification. of the invention, ghile Fig,. 10 is anendelevation as taken. at 1010 of Fig. 9- is;a side elevation of a. counter and disengageable. clutchmechanism in accordance with the: invention for connectingtheicounter to adrivingmechanism, Fig. 11 being avtransversesectionalelevation thereof as taken at 11-L1.of:Fig;. 12,. while-Fig.. 12. is an endelevat-ionas taken. at.1212. of Fig. 11.

Fig. 13 is.-a sectionalview oftheapparatus shown inFig. 11 taken. substantially along line" 1313;

Fig.. l4 shows the embodiment of the counter-.mecha, nismqofi Figs. 11-13. but modified by the inclusion of a.resetting.;mechanism, together with a clutch arrange ment;

Fig. 15' is. a? sectional view of the device shown. in Fig.. 14-. taken: substantially along; line 1515; and

Fig. 16 is also a: sectional. view of the device-shown in Fig; 14 taken-:substantially along'line..1616.-

Referring to:.Fig.; 1, the counter thereof, comprises av driveshaft.1,. journaled to a-sframe 2; Keyed to: the drive; shaft 1: by means of..a' pin. 3; isa'. lower indicia drum 4,. representing; ,for. example, units 'ofthe. decimal system, this drum bearing on its peripheral'face. equally spaced digits,. ranging. from 0- to 9,- as shown for the drumt23 at the left. The drum 4 has integral therewitlra'hub 5, whiclris eccentric togthe shaft. Journaled to the eccentriehub 5, andihence rotatable thereon,. is aplateor'disco, having, upstanding; from its left hand surface asviewed-in. Fig. 1, a: series of. nine. equally spacedpins; as at 7, disc- 6. beingz'hereinafter referred to.;as a:spur' gear. Journaled to and hence rotatably mountedom the drive. shaft 1,; adjacent the: drum 4,: is a. secondand higher indicia drum 8, similar to drum 4, having; cut or formed: in: its right. hand face, as viewed inMFig. 1', an internal. ring. gear' 9, provided with ten equally spaced, substantially semicircular notches or cutouts, as at 10, adapted to mesh progressivelyv with. the pins 7 ofzthe spur gear'6, asthe drive shaft is rotated, as described hereinafter.

Mounted. in..-the lower portion of the frame 2, is a shaft'll, which'parallels the: drive shaft 1, andto which is journaledsan; angle. shaped. pawl.12, one leg; 13 of which normally engages' a lug. 14' projecting from the outer-periphery of the spur gear 6: The other leg: 15 of pawl 12' has projecting fromtheleft hand facethereof, as-viewed in Fig. 1, a pin 16, Which'normally seats in .a notch, such as 17, of a ratchet face 18, formed in the outer'ri'ght hand. periphery of drum" 8; as viewed in Fig. 1. Angularly spaced from the projectinglug formedLon plate. 6,. is asecond lug. 19'havingprojecting therefrom apin. 20' to which one end of a tension spring 21 @is. secured, the opposite: end of this spring. being connected to a pin 22 projecting; from the leg 15 of pawl12.

If .desired, a third or.any=requisite additional/number of still higher indicia drums, such as 23, each similar to drums 4 and 8, may be journaled to the drive shaft 1, in the same manner as drum 8, and interconnected with each other in the manner above described with reference to drums 4 and 8.

In the operation of this device, as drive shaft 1 is rotatably driven in a clockwise direction, as viewed in Fig. 2, it will carry with it the first drum 4 keyed thereto, thus causing the pins 7 of the spur gear, rotatable on the first drum eccentric 5, successively to engage notches 10, of the internal ring gear 9 formed on the next drum 8 Thus starting from the position shown in Fig. 2 with pn 7a seated in notch 10a, the meshing will progress in the direction of pins 7b, 7c, etc., seating successively in the notches 10b, 10c, etc., thus progressively to rotate the spur gear 6, in a counterclockwse direction, until the drive shaft 1 has completed nine-tenths of a complete revolution, in which position the pin 7a will be in the position 7a for seating in the notch 10 of the internal ring gear 9. This counterclockwise displacement of plate 6 as the drive shaft is rotatably driven clockwise, results from the fact that the second drum 8, is locked against rotative movement by the seating of the pin 16 of pawl 12 in a notch 17 of the ratchet face 18 of drum 8. As the spur gear 6 is thus rotatably displaced counterclockwise, the projecting lug 14 thereof will ultimately engage the pin 16 of pawl 12, at the instant that pin 7a of plate 6 seats in the notch 10 of the internal ring gear 9. Also as the spur gear 6 is thus displaced, the spring 21 extending between lug 19 of plate 6 and arm 16 of pawl 12, is increasingly tensioned, so that when lug 14 of plate 6 engages pin 16 of the pawl, and thus disengages this pin from the ratchet face 18, drum 8 will be rotated one-tenth of a turn by the restoring action of spring 21, which now rotates plate 6 clockwise, as pin 16 slides along the adjacent face 18a of the ratchet, and ultimately seats in the succeeding notch 17a thereof to arrest the further movement of drum 8. It should be borne in mind in this connection that since pin 7a is now seated in notch 10 of drum 8, the clockwise rotative movement imparted to the spur gear 6 by the restoring action of spring 21, is thus transmitted to the drum 8, thereby correspondingly rotating the latter A of a turn.

This sequence of operations is continued for each complete cycle of rotation of the drive shaft 1, carrying with it the lowest indicia drum 4, until the second drum 8 has been stepped around to successive extents of onetenth turn each, until drum 8 has completed a cycle of rotation, at which time pawl 24 of the drum will be actuated in a manner similar to that above described with reference to pawl 12, whereby drum 8 now rotates the next higher indicia drum 23, one-tenth of a turn or one digit thereon.

Thus in the embodiment of the invention above described, since there are nine pins such as 7, in each spur gear 6 of a lower indicia drum, and since there are ten notches such as in the internal ring gear such as 9, of each next higher indicia drum, such as 8, the spur gear 6 will creep in anticlockwise rotation by one-tenth of a turn, during nine-tenths of the turn of clockwise rotation of the drum on which such spur gear is mounted. But since the spur gear 6 is under tension of the spring 21, and the lug 14 of this gear will have traveled by onetenth of a turn anticlockwise to displace the pin 16 of the pawl from the ratchet face 18, the spring will thereby be free to pull the spur gear 6 and with it the second drum with which that plate meshes, back to the position shown in Fig. 2 of the drawing, by clockwise rotation, thus to rotate the next higher indicia drum one-tenth of a turn or one digit, in the clockwise direction. That is to say, each complete revolution of the shaft 1, and consequently the first drum 4, will produce one-tenth of a turn of the next adjacent drum 8. And each complete turn of the second drum 8 will produce one-tenth of a turn of the next higher drum such as 23, and so on irrespective of the number of digital drums mounted on shaft 1.

It is further to be noted with this modification that the counterclockwise angular shifting of each spur gear, such as 6, occurs during nine-tenths of a complete revolution of the preceding drum, during which energy is stored in the spring 21, which is employed on the carryover of the next higher indicia drum, following the last one-tenth turn of the preceding drum.

Another feature to be observed with respect to this construction is that the backward creep of the spur gear 6, which is obtained in counting devices heretofore known, by means of compensating cams and even more complicated constructions, is secured in the above modification, by the simple expedient of retaining the next higher indicia drum, by means of the pawls such as 12, against rotation during nine-tenths of a turn of the next lower indicia drum.

In the next modification of the invention to be discussed, namely, that illustrated in Figs. 3 and 4, each higher indicia drum is retained immobile during ninetenths of a revolution of the next lower indicia drum, by means of a Geneva cam.

Referring now to the Figs. 3 and 4, this modification of the invention comprises a high speed counter, which can be extended to include a large number of indicia drums, for counting up to any desired magnitude, because it embodies a backlash compensating mechanism.

In this modification the drive shaft 31, is again journaled in a frame 32. Keyed to shaft 31, are a driving gear 33, and the lowermost indicia drum 34. Drum 34 has integral therewith an eccentric hub 35, to the outer end of which is journaled a spur gear 36, which is thus rotatively free on the eccentric. This gear is provided on its outer face with a series of nine equi-spaced teeth, as at 37.

The next adjacent higher indicia drum 38, is generally similar to drum 34, except for being journaled to and hence freely rotatable on the drive shaft 31. Drum 38 has hollowed out of its face 39, opposed to drum 34, an internal ring gear 40, consisting of ten equi-spaced teeth, such as 41, alternating with notches or depressions. as at 42. The spur gear 36 is mounted in meshing relation with the ring gear 40, in the manner shown most clearly by the dotted contour lines 37, 41, 42 of Fig. 4.

As in Fig. 4, gear 36 has formed in its peripheral edge, a pair of similarly shaped depressions or notches, 43, 44, which are angularly spaced, to provide therebetween, a prong or tooth 45. Mounted on the first driven hub 35, adjacent gear 36, is a second plate 46 shaped to form a prong 47 similar to prong 45 of gear 36, this plate having the configuration in plan shown by the contour lines 48 of Figs. 4 and 8, and the prong 47 thereof being superimposed in the former showing on the prong 45 of gear 36, these prongs being mounted in contiguous but sliding surface engagement, as shown in Fig. 3. Also mounted on the first driven hub 35, is a cam 49, having the contour shown in full lines in Fig. 4. The prong 47 and cam 49 are keyed to the hub 35, as at 50, and hence rotatable therewith.

Mounted in the lower portion of the frame 32, is a shaft 51 which parallels the drive shaft 31. Journaled to shaft 51, is a carry-over member 52, which partakes of an oscillatory movement as explained below, and which has integral therewith a pair of spaced prongs 53, 54, positioned respectively to enter the notches 43, 44, of gear 36, with the prong 45 thereof disposed between the prongs 53, 54 of the carry-over.

Formed on the backside (Figs. 4 and 5) of the carryover 52, is a Geneva cam 55, having an arcuate cam face, as at 56, adapted to engage complementary arcuate, Geneva cutouts, such as 57, formed in the peripheral edge of the next higher indicia drum 38. These cutouts are best shown in side elevation at 58 for the still next higher indicia drum 59 of Fig. 3.

In the operation of this device, assume that the various components described are in the relative positions shown in Fig. 4. If now the drive shaft is rotated clockwise, it will rotate therewith, the drum 34, the prong 47, and the cam 49, since all of these components are integral with the drive shaft. As these components are thus rotated clockwise, the spur gear 36 will be rotated slowly counterclockwise, due to progressive engagement of the spur gear teeth 37 with the depressions 4-2 in the internal ring gear 40 of the next drum 38, inasmuch as this drum 38 is locked against rotation by engagement of the carry-over Geneva cam 55, with one of the Geneva cutouts 57 of drum 38. This counterclockwise rotation of the spur gear 36 will rotate the carry-over 52 clockwise, by engagement of the prong 45 of the spur gear 36 with the prong 54 of the carry-over.

During nine-tenths of one complete revolution of the drive shaft, the spur gear 36 will thus be rotated counterclockwise, by one-tenth of a complete revolution of the drive shaft, and will thereby rotate the carry-over 52 mmaaganr ate i'the -':extent :that :prong 54 will assume the dotted *line position shown at 54a, while prong 53 will assume the ,xprevious position i of :prOHg 5.4. .As :the :drive shaft :con-

:tinues :to :beflrotated Ithrough :the final one-tenth .of .its

complete cycle, tthelleading-edgetof thecam 49 -will en- :gage.the.carry=over;prong:54 and further rotate.it clockwise (Fig. 4) to position 54'b,. sufiicientlyifor the arcutaterface 5,6:ofIthetcarry-over Geneva team '55 to-swing tClflaI' Of theitooth 57, separating :the .Geneva cutouts 57 :of :drum 238, .in which the .cam .55 has "been engaged, i-thus freeing :drum $38 for :rotation. 'Thereupon, while so freed, and .as the clockwise rotation 'of the 1 drive shaft :31 :continues, athe prongAl, rotating 'with the :drivezshaft vamd drumr38, will engage the arm :53 of the carry-over, and swing it quicklytback, y:.counterclockwise rotation, tto thez'full line position sh'owniinFig. 4, thus'restoring the icamyaover 10 its initial setting.

thexarryeoverxis .thusrswung back, it carries with .itsthe :spurigear36, by a clockwise angular shift of the ';latter, :due 1.to engagement vof the :carr-y-overarm 54 with xthezspur gear prong 45. .And'since the'spur gear 36 is in aneshingtengagement wit -.the drum :38, .and :since drum .38 will :be :rotated by one-tenth :of a turn, but will :be prevented :from :rotating due to .the .fact Ethat the 'arcuate 'face 56 of the carryrover vGeneva cam 55, :is now in engagement with the /arcuate .face .of the :next succeeding Geneva cutout 57 1oftdruml38.

All components of 'the first counter drum 34 have thus been :restoredto the relative positions shown in Fig. 4, and vthe second drum 38 has been'rotated one-tenth ofa turnsor one digit. Thisisame cycleof operations is rrepeated .over :and :over again for succeeding revolutions -.of :the 'driveashaft 3,1, each =revolution thereof stepping 'the second'counter drum around one digit, in themanner above described.

By identically the same sequence of operations the second counter drum 38 steps 'the next counter drum 59 around one-tenth of a turn or one digit, for each succeeding revolutionofcounter drum 38, and so on for .any number :of additional counter drums journaled to the .drive shaft 31.

The 'cam 49 serves to prevent --locking of the carryover through-backlash. 7 Thus suppose that through backlash, the :prong54 of the carry-over would not, in the absencetof cam 49,-quite reach the position shown by the .dotted iline 54b, and thus would be slightlydelayed in reaching that position. In that event, the cam 49 will force it .into :that position, .in Big. 3, the sthickness of the carry-over prong '54'extends into theplane of team 49, whereas this cam isvdisposed in :a plane above that of the carry-over prong 53, sand hence clears the same,.so that prong 53 of the carry- :over .1s=onlyaengaged vby prong 45 .of'thespur gear 36. I

ilShe ;earr.y-;over'prong 54-also.meshes with theother side of:s pur.gear.prong '45, and in addition extends into the plane of cam 49, to be actuated thereby as aforesaid.

-10peration :ofxthe mechanism may beimproved by the addition :of a .tensioning spring :60, stretched between a :pin 61 :on1the :carry-:over and a fixed support 62, to impart additional :impetus thereto during the-carry-over.

Thetcounting deviceof this-modification of the invention ipossesses a .verysstrong :carry-over part, instead of the ,small and delicate part usually .countingtdevices, but :one which, nevertheless, occupies :no-more space than the aforesaid delicate parts of said z-prior devices, because the :actuating carry-over mechany additional amount because, as is clearly shown encountered in other 1 r .anism -is disposed within the peripheries of the counting drums.

The modification shown in Figs. 9 and 10, comprises zasdri-ve shaft .71, journaled in a frame 72. Keyed to the .drive shaft is a hub '73, on which is mounted a drum 74 secured to the hub. As shown in Fig. 9, this drum preferably comprises a pair .of cup-like, thin, sheet metal stampin'gs, 74:2,7412, fitting one within the other and securedtogether. ,At its left extremity, Fig. 9, this drum has formed therein, an eccentric 75, on which is rotatably mounted a flat, 'spur gear 76, having nine teeth on its outer periphery, as at 77. This spurgear meshes with an internal gear of ten teeth, as at 78, formed in the :opposed face of the next drum 79, the latter being joun nailed toand hence rotatable on shaft 71.

Projecting'from the -faceof the spur gear 76, opposed to that of drum 74, is a pin 80, which is engaged in a 6 .slot'281iofza carryeoverzpart 82. .This carryeoverzpart is simply a :sheet .metal :-stamping, :bent over 'on :its .self tas is'hownzin Fig. 9, .to .provide,'in difieernt planes,"thess'lot- 'zlike opening :81 and za pair Of oppositely disposed ilegs 83a, 84b. The carry-.oversis pivotally mounted, as;'at :84, :on :a .shaft :85, 'L'the latter :being :rnounted Im the frame .72, in the -:manner shown in Fig. :9. iThe'carry- :over 82 Zis:interp.osed.betweemthe first drum 7.4 andithe spur :gear .76, with the tpin 80 :of the latter :engaging ;the=-sloti81 of fthe'carr-yfoverz-as above explained.

Projecting .from the left .tface, .Fig. ;9, :of :the :drum .74, is .a pin 86, adaptedttoiengage-the legs .8311, 18311, :of .the carry-over, as explained below.

\With athe mechanism .as thusjfar :described, :and assuming the second adrum .79 vto be .held zimmobile, .when '-;the drive shaft 171, Land withritzthe first drum 74,:is:rotated clockwise, :Eig. .llO, from the initial position :shown, :and through n'ine-tenths .of ;a complete revolution, .the spur gear '.:'7.6 -will :be :.rotated counterclockwise .by one-tenth of a turn. In so doing, it will swing the carry-.over182 in :.a :clockwise :direction, from ;the position sshown in .the drawi g, tOza .position=wherein;leg 83b occupies :the position shown .for.leg 83a, due 'to engagement-of :the 'spur gear pin .80 :with 'the slot 81 of the tcarry-over. Thereupon the pine aof the gfirst .drum 74, will, during theifinal one-itenthof the revolution of this drum, -.enter between :the ;legs 83a, 83b .of .the :earry-over, 1and ;by engaging the inner edge .of .leg 83b :thereof, thus swing .the .carry-over :rapidly back to its initial position, &as shown in Fig. 110. .Jn thus .beingswung back to itssinitial position, .the -.carr yover will now .rotate the .spur gear .76 clockwise, and since this spur gear is in meshing ;engagement .with the internal .gear .of :the second :drum .719, ithersecond :drum will;a1so*.be rotated through tonevtenth of :a turn, .orzin :the :amount toftone zdigit.

The :mechanism for ;holding alhf: zsecond :drum 79 timmobile except during -:the .carry-over will now the described. :Between IhCICaIIYvDVGI' :82 and :thespur gear 76, there is interposed a plate 87, of elongated configuraztion,aspshowndndiig. 10. This :plate:has:formed in its opposite ends, :longitudinally :;extending .cutouts or :slots, as at 188, :and is ,mounted for :longitudinal displacement :between -the:,aforesaid shaft :85, carried :by frame .72;at -.the atop ithereof, sand a similar shaft :89, carried by .frame 72 at :the base thereof. .The-p1ate.-87 extends tbetween zthe shafts 85, $89 with .the ,-longitudinal cutouts, ;such as 88, engaging these shafts, respectively. The plate :87 is also :provided with .a central aperture :90 .of the con- .figurationshown in Fig. :10, and through this aperture, the ;pin 8.0:of-the-spur gear 76,:extends intothe carryover .slot .81.

The ,left :side .of drum 74, as viewed in Fig. :9, has formed therein an indented cam track 93, .ofzroughlyfishaped configuration, as sshown :in .Fig. 10. Into this cam track :extends ;a pin .94 mounted on :the right face, .Fig.,-9, .of thespurtgear .76.

:Assuming nowthat thecomponents of the icountenare :initially in .the'relativepositions shown in Fig. 10, the .driveshaft T1, and with it the :first drurn 74, is .turned;a .little less than one-tenth .of -a turn in the-clockwise .direction, the:pin :86 on drum 74,-will travel alongside of the curved :inner ,face of the carry-over leg :83b, thus preventing thec-arry-overfrom swinging .to the left. 'The ,carryrover ,:is already prevented :from .swinging to .the right, because .the pin :80, :which extends .into the .cam slot 81,thr.ough the plate 87, .is stopped against'the right hand .side -of the opening 90 in this plate. Thus, the carry-over ;82, .and consequently thenext drum 79, are locked imposition, relative to each other, throughout nearlyone-tenth of a.turn,-of the first drum. .Asathesystem is symmetrical, thevsame is true for the opposite .dilifiCtiQItOf rotation of;the first drum 74.

:In view ofthefact that :the:carry1over82is thus-locked in position throughout substantially two-tenths of :a revealution :of the first drum .it is thus established that the second drum 79 .need'onlybelocked in positionduringa :little :more :than seven-tenths .ofa turn, being thereupon freed .to-rotate 'for theremaining one-tenth of a turn, :to permittthe carry-over-to actuatethe same as above stated. To;lock-:the second drum 79 during this remaining seventenths of'arturn, the plate 87, is driven downwardly, by the .action of the .cam track '93 in the preceding drum randrthe pin 94.ofithe;spur gear, engaging'this cam track. .As the plate 87 is :thustdriven downwardly, "lugs 95, Fig. 9,ton :'the tleft :side 'and..at.opposite ends of .the plate 87,

' engage one of a series of ten notches 96 formed. about the periphery of drum 79, whereby the plate 87 locks this drum in position, until the plate is subsequently driven upwardly again by the action of the cam track 93 and the pin 94 coacting therewith.

During this remaining seven-tenths of a turn of the first drum, the spur gear 76, will, of course, be free to rotate on the eccentric 75 of the first drum, and will thus swing the carry-over 82 to the left from the position shown in Fig. 10, until, as above stated, the right leg 83b thereof, occupies the position shown for 83a. Thereupon, and as above stated, the pin 86 of the first drum 74, will, during the final one-tenth of the revolution of this drum, enter between the legs 83a, 83b of the carry-over, and by engaging the leg 83b thereof, will swing the carryover rapidly back to the position shown in Fig. 10, during which interval the second drum 79 will be unlocked, due

' to upward displacement of the plate 87, by virtue of coaction between the cam track 93 and the pin 94 engaging the same.

Still referring to Fig. 10, and starting with the position of the components as shown in this figure, it will be observed that during the first one-tenth of a turn of the first drum 74, the spur gear 76 cannot rotate counterclockwise, to any substantial degree, as it should, since during the interval the carry-over is locked in position in the manner above explained. The counterclockwise rotation of the spur gear fortunately starts very slowly, but picks up speed as the first drum continues to rotate and the pin 86 thereon swings clear of the carry-over leg 83b. Thus, for the first one-tenth of a turn, the counterclockwise rotation of the spur gear is very small, but increases progressively in rate of motion for each additional onetenth turn up to the fifth one-tenth. Thereupon, its rate of rotation decreases in the same proportion at it previously increased. This permits the plate 87 to lock gradually onto the second drum 79, as it is driven downwardly by the cam track and cam 93, 94 in the manner aforesaid.

It will be observed that this counter works in both directions of rotation, to add or subtract digits, whereas the counters of Figs. 1 to 4 embodiments, work only in the additive direction. Also in the embodiment of Figs. 9 and 10, the higher indicia drums, are firmly locked in position, except during the carry-over period. Also, and contrary to previously known counters, by reducing the dimensions of the structure, none of the parts become too small to be stamped, so that instead of the die cast or heavy metal constructions required in previous counters, the components of this counter can be stamped from exceedingly thin sheet metal, which makes them very light in weight and reduces considerably the requisite torque applied thereto.

Figs. 11 to 13 inclusive show a modification of the invention wherein the counters may be quickly and easily cancelled, i. e., restored to their zero settings. Mounted upon the first eccentric is a finger 105, which is secured to the eccentric, as at 106, this finger having the configuration, in plan, as shown at 107, Fig. 13, which latter represents the corresponding figure for the second drum 108a. Rotatably mounted on the first eccentric 100 is a spur gear 108, provided with nine peripheral teeth as at 109, the depressions between which, such as 110, are engageable by a pawl 111 as explained below. Also the spur gear 108 is provided on its left face, Figs. 11 and 12, with nine equi-spaced upstanding pins, as at 112, adapted successively to seat in corresponding depressions or notches, such as 113, formed in the right hand face, Fig. 11, of a flanged extension 114, of a second eccentric 115 on which a second drum 108a, is angularly shiftable. This eccentric 115 is rotatable on the drive shaft 102. Such internally notched extension and said rigidly mounted pins constitute internal gear with planetary gear means.

The pawl 111, which is arcuate shaped, as shown in Fig. 12, is pivotally mounted, at its approximate center, on a shaft 116, fixed to the frame of the counter in a manner generally similar to shaft 51 of the Figs. 3 and 4 embodiment. This pawl has a hook-like terminus, 117 at its right end, Fig. 12, which is seatable in the depressions 110 of the spur gear 108, and in the manner illustrated in Fig. 12. This terminus 117 of the pawl has mounted thereon a pin 118, which projects from its under side, Fig. 12, and is engageable in the notches, such as 119, of a ratchet face 120, cut or formed in the right ha181d peripheral surface, Fig. 11, of the second drum 10 a. i

The opposite hook-like terminus 121 of pawl 111, is offset as at 122, from the plane of the terminus 117, and is engageable in a single notch 123, formed in the peripheral edge 136 of the flanged extension 114 of the second drum eccentric 115.

Referring to Figs. 11 and 13, the radially extending face 124 of the second drum 108a is arcuately slotted as at 125, and through this slot a pin 126 extends from the hub flange 114, on which this pin is mounted. Secured to this pin is an upstanding lug 127, to which one end of a tension spring 128 is secured, the opposite end of this spring being secured to a pin 129 upstanding from the radial face 124 of the second drum.

Referring more particularly to Fig. 13, it will be observed that the drive shaft 102, is longitudinally notched as at 130, in such manner that upon rotation of the shaft in the clockwise direction, Fig. 12, as to seat in the notch 130, a pawl, such as 131, pivotally mounted on the exposed face of each eccentric 100, 115, etc., as at 132, the free end of pawl 131 being resiliently held against the shaft 102 by means of a spring, such as 133, also mounted on the face of the eccentric, as at 134.

in the operation of this counter both the spur gear 108 and the second drum 108a, are prevented from rotating during nine-tenths of each revolution of the first drum 103. This results from the fact that the end 117 of pawl 111 is normally seated in a depression of the spur gear 108, while the pawl pin 118, is normally seated in a notch 119 of the ratchet formed on the second drum 1084:. After nine-tenths of a turn of the first drum 103 and eccentric 100, the finger 105 integral with the first drum, trips the pin 118 of pawl 111, thus releasing the second drum 108a, which is thereby rotated one-tenth of a turn, or the amount of one digit, by virtue of the restoring action of the tension spring 128.

To trace through the operation: Assume, referring to Fig. 12, that the finger 105, is disposed on the right hand side of the pin 118, and that this pin is now seated in a notch 119 of the second drum ratchet in the manner shown in Fig. 12. Let a driving force be applied to drum 103 to rotate the shaft counterclockwise, as viewed in Fig. 12. During the ensuing nine-tenths of a complete revolution, the teeth or pins 112 of the spur gear 108 will progressively engage the notches 113 of the eccentric 115 of the second drum, whereby this eccentric will be rotated clockwise, as viewed from the right in Fig. 11, thus to tense the spring 128. During this movement of the second drum eccentric 115, the second drum 108a itself will remain stationary, as will also the spur gear 108, the former due to the seating of the pawl pin 118 in the second drum ratchet face 120, and the latter due to the seating of the pawl lug 117 in a depression 110 of the spur gear 108. Referring to Fig. 13 the effect will be for the pin 126 to move to the left ilzosng the arcuate slot and thereby tense the spring Upon completion of the first nine-tenths of a complete turn of the first drum, the finger 105 thereof will be slightly to the left of the position shown in Fig. 12, and will thereupon engage the pawl pin 118 and knock it out of the second drum ratchet notch in which it is seated. This releases the second drum as a result of which, due to the restoring action of the tension spring 128, the second drum is rotated one-tenth of a turn, and until the pawl pin 118 seats in the next succeeding notch 119 of the second drum ratchet. By this time the finger 105 of the first drum has passed beyond the pawl pin 118, whereby this pin automatically seats in the next succeeding ratchet notch.

For resetting the counters, shaft 116 is manually rotated, until the lug 121 of each pawl 111, engages the helical face 136 of the flanged extension 114 of each eccentric drum hub 115. This frees the spur gears 108 for rotation, and hence also the eccentrics. The reset shaft 102 is now rotated clockwise, Fig. 12, whereby the pawls 131 for the successive drums engage the drive shaft notches 130, following which all drum eccentrics are driven, and with them the drums, until the end 121 of the pawl for each drum, engages the notch 123 of the associated eccentric. When the pawls 111 are again allowed to rotate until the fingers 117 of each seat in a notch 110 of their associated spur gears 108, all counters will be restored to their zero settings.

sgauagsrw Figsa}. 1.4; and: 1.6ill'1ClUSiVC,xShOWZ the. same; counter era-.-

b'oidying. a; resetting mechanism, anch also a..novel clutch' arrangementifor driv ng thee counter. Like elements are similarly. designated m2 these; figures; The construction andioperation'of the: counteripropersiscthe sameas that provided, about its periphery, with axpluralityv of notches as at l'53';.while the second drum 152; isprovided'i about its peripherywith: a 2 different plurality of resilient fingers, as at.154,- engageable; one ata-tirnerin the notches 153, since asexplained below, the-fingers and notches are relatively so space'd'as' to have no common factor;

Theclutch drums. 150 and 152 are concentric: with the. counter drive" shaft 102, drum 150 being. journaled thereon as: stated; while drum 152 is: axially but not rotatively keyed thereto as at 155', whichcan rotate in an annular space provided in 152; Integral with drum 152 is a pinion'gear 1'56 for'driving this drumby means of a driving gear157 rneshing'therewith'. A helical compression spring 158; surrounding shaft 102 is interposed between theclutch drums'1'50'and' 152, or facilitating disengagement thereof as explained below: Mounted on the-opposite end of the counter shaft 102, 1s-a knob 158a having therein' a peripheral notch 1S9;

engageable by a pin-160 of alever arm' 1'61 the-other'end' of which arm is keyed as at'162 to shaft 116 of the counter. Pin' I60 projects beyond the=plane of the knob 1'58a, in the mannershown' iniFig; 14, to provide a grip for depressing the lever to the dotted line position 161?; ofFig. l6, thus=to disengage the lever'fromtheknob, and to rotate shaft 116 =and thepawls111tz and 11112.

With' the lever 161" thus depressed; the knob 158a ma} be pushed" to the: right (-Fig; 14) carrying with it the counter shaft 102; thus-to disengage the-clutchdrum 152" from the. clutch drum 150. Engagement" is again effected bypulling the knob 158a to the'left against the" compression action of' 'thespring 158 interposed" between the clutch drums;

It will be observed' that sincethe: lever arm 161' is keyed to'the-shaft116', on-which are'mounted the pawl's 111a; 11"1'b, etcz, described'with reference toFigs. 11 to 19inc that'this releasesthe=counter drnms'103, 103a, 1031;, for resetting, in themanner above described with reference to Figs. 11 to1'3; this-cancellation being effected by rotation of the knoh'158a;

When shaft 102 is'pushed' to' the right" the pin 163' disengages a notch I6'4'inthe frame' 1642:; During the rotation of shaft 102' thesurfacecf'the frame 1-64aprevents the shaft 102from sliding to theleft' untilrotation' is" completedf In 'this waythe clutch remains? disengaged;

Now reverting to" the clutch mechanism, it will be noted'lthat in the specific" embodiment" shown, that the clutch drunr 152-is provided with seven equi spaced'fingers 154; while drum. 150* isprovided with twelve equi Since there are thus seven fingers spaced notches" 153i on-drum15-2' and twel've notches' on drum=150 theyhave' no=common factor, so'that whatever'theii'Telativerotafive positions, it'is impossiblethat at: least". one of the clutch-fingers willbefurther away from anotclr than one' over 7x12 or 4 ofa turn. Thesameistrue for'other combinations of numbers which havenocommon factor, so that the errorin'rotative displacement-cf clutch member'1'52' with respect to clutehmember'150; before' one' of" the fingers of the former engages a notch of the latter; as-at 1'65, can bemad'e as smallas desired; Also itwill be observedthat'when' engagementis'thus effected the-clutch' drums are'lockingly rather than merely'fric tionally engaged with one another.

What is claimedis:

l. Ina counting device: a first'and lower indicia drum; a second and higher indicia drnmgan eccentric angularly shiftablewith said first drum; internal gear means and.

meshing planetary gear means operatively associating said= eccentric. and. second.v indiciadrurn whereby. angular-r motion. of. said eccentric. in. one. direction. angularly shittsone of. said gear'meansin the opposite direction; detent. means for holding said second indicia. drum aga1nst rotation during; a: preselected angular'shiftof said eccentricin such first direction; means fon rendering. momentarily inefiiectivef saiddetent meansf in response; to such preselected: angular: shiftv of. said eccentric, andmeansfor; advancingmaidisecond tindicia drum: when said detent means. are: so: momentarily ineffective.

2. I'n1a countrngdevme: a. first and'lower ind1c1a drum; aasecond-and-hlgher ind1c1a drum; a. shaft forv mounting said drums; an eccentric-on said shaft angularly shiftable-with-said first drum; internalv gear means and meshmgv planetary gear meansoperatively associating said .eccentricand'second indicia drum whereby angular motion ofisaid eccentric in. one directionangularlyshifts-one i of said-gear means'in thetopposite direction; detent means forholdingsaid secondzindicia drum against rotation during a preselected angular shift ofrsaid eccentric in such firstv direction,.detent shiftingmeans, said detent means being momentarily rendered ineffective by. such. detent shifting means which are angularly shiftableinresponse tomotion of said eccentric; andmeans for advancing said. second indiciadrurn when .said.=detent. means are. so. momentarily inefiective.

3. In a counting device in combination: a first and .lower indicia drum,.a.secondland higher indiciadrum, a

shaft integral with. said first. drum,.an eccentric integral withsaid shaft, aspurgear. journaledtosaid.eccentric, an internal. ring. gear: integral with.said second drum, said spur. gear havingoneless tooththan-saidringgear and meshing therewith, aratchet cutout.extendingperipherally about the. second. drum,.an.angular pawl. pivoted at its apex andhavingapinsecuredto one legengaging said ratchet, saidspur gearhaving aprong normally engaging asecondleg. of. said pawl,. a.tension spring. linking saidspur gear to saidfirstpawlleg, wherebyrotation of saidfirstdrum in onedirectionrotates said spur gear. in the opposite; direction. untill the prong thereon: engages saidpinonsaidlpawlrto. disengage. the latter from said ratchet. whereupon. said tension spring. rotates said. spur gear and. the. internal. ring. gear. on such. second drum.-

meshed therewith into engagement respectively with the second. leg. of said pawl. andsaid pin, said second drum having. been. thereby. angularly advanced one ratchet tooth..

4. An intermittently actuating reduction. gear mechanism comprising.- a-driving.shaft,.an eccentric and a cam integraltherewith, .a spur gear. journaled on said eccentric, a drivenmember. journaled. to. said. shaft and having integral. therewith. an. internal ringgear meshing with said spur. gear, saidlspur gear havingone-less tooth than said rmg gear, .a.carry,-over. member. journaled'to a-shaft paralleling. saiddrive. shaft,. a disc. integral with said spur gearhavingapair. of spaced-cutouts in the peripheraledge thereof. forming aprong therebetween, said carry-over member. having va pair. ofiradially extending prongs P051.

tionable respectively in said cutouts with said disc prong. therebetween, a. disc. integral with. said driven member havingGeneva cutouts;in itsperipheral edge, a Geneva cam. on..said carry-over,.positioned to engage said cutouts,. and a.cam integralwith said driven shaft adapted duringrotation thereof toengage for a. portion of each cycle. of rotation,-. one prong. ofl said carry-over thereby torotatethe. same through a..small.angle, whereby upon continued. rotation. of. the. drive. shaft. in. one. direction, saidspur gear. isoppositely rotatedthereby to rotate said carry-over until. theGeneva cam. thereon is. disengaged froma cutout of. said. Geneva cam, whereupon tsaid cam integral: with said. drive shaftv engages. one leg. of said: carry-overand thereby rotatesthesame. and with itsaid. pronged disc and. spur/gear until said Genevacam engages and seats in.the.succeeding.= cutout ofsaid. Geneva Cam 5. In acounting device-incombination: a-drive shaft,.

a first and lower indicia. drumdntcgral. with said. shaft,

a. second andhigher indicia drum adjacentthereto and member interposed between said drums, and. means.

mounting the. same: for. oscillating, rectilinear displacement, said-cam membershaving a central aperture through 86 which. thepin. secured. to said spurv gear. extends, a. pin

secured to said spur gear and a cam slot formed in said first drum engaging said pin, said cam and carry-over member so cooperating as to prevent rotation of said second drum only for a preselected interval of a complete cycle of rotation of said first drum.

6. In a counting device the combination: a first eccentric having a first drum secured thereto, a trip finger secured to such eccentric for angular motion therewith, a spur gear journaled upon such first eccentric, such spur gear having a plurality of peripheral teeth, a second eccentric angularly shiftable about a common axis with said first eccentric and having an internal ring gear formed in one face of a flanged extension thereof, a second drum journaled upon said second eccentric and angularly shiftable thereupon, said spur gear having a plurality of pins secured thereto one less in number than the number of teeth in said internal ring gear, the number of teeth of said spur gear being equal to the number of such pins, said second drum having a ratchet surface extending peripherally thereabout, a pawl member pivoted intermediate the extremities thereof and having a pin secured to one leg for engaging said ratchet and also having a hooklike terminus at one extremity settable between the teeth of such spur gear whereby such second drum can be held against angular motion in one direction and said spur gear can be held against angular motion in either direction, the opposite extremity of such pawl having a secondary hook-like terminus offset from the plane of the first-mentioned terminus, the aforementioned flanged extension of the second eccentric having a single notch in the periphery thereof for engaging said secondary offset hook-like terminus, means for resiliently holding said second drum in a preselected angular relation with such second eccentric upon which it is journaled whereby such drum is angularly shiftable but is urged toward such preselected angular relation, 2. drive shaft for supporting said eccentrics, rotation of said first drum in one direction being effective angularly to shift said second eccentric in an opposite direction thereby to tense the aforementioned resilient means, said second drum remaining stationary until said trip finger engages said pin on said pawl thereby to disengage same from said peripheral ratchet on the second drum whereupon said resilient means angularly advances said drum one ratchet tooth, and pawl means associated with each of said eccentrics and such shaft whereby such eccentrics are rotatable together by rotation of such shaft in one direction of angular motion, whereby said drums can be shifted to a preselected norm in response to such shaft rotation when said secondary ofiset hook-like terminus is in engagement with the peripheiy of said flanged extensions.

7. In a counting device the combination: a first eccentric, a first drum mounted for rotation with said eccentric, a spur gear journaled upon such first eccentric, such spur gear having a plurality of peripheral teeth, a second eccentric angularly shiftable about a common axis with said first eccentric and having an internal ring gear formed in one face of a flanged extension thereof, a second drum journaled upon said second eccentric and angularly shiftable thereupon, said spur gear having a plurality of pins secured thereto, at least one less in number than the number of teeth in said internal ring gear, said second drum having a ratchet surface extending peripherally thereabout. a pawl member pivoted intermediate the extremities thereof and having a pin secured to one leg engaging said ratchet and also having a hook-like terminus at one extremity for engaging such spur gear whereby such second drum and such spur gear can be concurrently held against angular motion, means for resiliently holding said second drum in a preselected angular relation with such second eccentric upon which it is journaled whereby such drum is angularly shiftable but is urged toward such preselected angular relation, rotation of said first drum in one direction being effective angularly to shift said second eccentric in an opposite direction thereby to tense the aforementioned resilient means, and ratchet pin trip means angularly shiftable with said first drum, said second drum remaining stationary until said trip means engages said pin on said pawl thereby to disengage same from said peripheral. ratchet on the second drum whereupon said resilient means angularly advances said drum one ratchet tooth.

8. in a counting device, the combination: a first and lower indicia drum, a second and higher indicia drum, a pair of eccentrics one for mounting each of such drums,

shaft means for coaxially mounting said eccentrics, said first drum being secured to said first eccentric for angular motion therewith, a spur gear journaled upon said first eccentric for angular motion relative thereto, a pivotally mounted pawl, said spur gear having a plurality of pins secured to one face thereof, said pins being equal in number to the number of teeth of such spur gear, said second eccentric having a face in which is formed an internal ring gear having a number of teeth, at least one greater than the number of said pins, said pins being secured equidistant about the center of said spur gear and positioned for engaging the teeth of said internal ring gear, said second eccentric being angularly shiftable relative 'to said shaft means, said second drum having a peripheral ratchet formed thereabout, said pawl having a projection upon one of the legs thereof for engaging such peripheral racthet concurrently with the engagement thereof with said spur gear thereby to hold said drum and spur gear against angular motion, a trip finger secured to said first eccentric for angular motion therewith and positioned for disengaging said projection from such ratchet thereby to free such second drum for angular motion but concurrently holding said spur gear against angular movement, a tension spring linking said second drum and said second eccentric, whereby rotation of said first drum in one direction with said peripheral ratchet and spur gear engaged by said projection and pawl, rotates said second eccentric in an opposite direction until such trip finger engages said projection to disengage the latter from said peripheral ratchet whereupon said tension spring by its restorative action advances said second drum and the ratclliet thereof into engagement with another ratchet toot 9. In a counting device, the combination: a first and lower indicia drum, a second and higher indicia drum, a pair of eccentrics one for mounting each of such drums, shaft means for coaxially mounting said eccentrics, said first drum being secured to said first eccentric for angular motion therewith, a spur gear journaled upon said first eccentric for angular motion relative thereto, an angularly shiftable pawl pivotally mounted intermediate its extremities and having planar offset termini, said spur gear having a plurality of pins secured to one face thereof, said pins being equal in number to the number of teeth of such spur gear, said second eccentric having a face in which is formed an internal ring gear having a number of teeth, at least one greater than the number of said pins, said pins being secured equidistant about the center of said spur gear and positioned for engaging the teeth of said internal ring gear, said second eccentric being angularly shiftable relative to said shaft means, said second drum having a peripheral ratchet formed thereabout, said pawl having a projection upon one of the legs thereof for engaging such peripheral ratchet concurrently with the engagement by one of the termini thereof with said spur gear thereby to hold said drum and spur gear against angular motion, a trip finger secured to said first eccentric for angular motion therewith and positioned for disengaging said projection from said ratchet thereby to free such second drum for angular motion but concurrently holding said spur gear against angular movement, a tension spring linking said second drum and said second eccentric, whereby rotation of said first drum in one direction with said peripheral ratchet and said spur gear engaged b said projection and termini, rotates said second eccentric in an opposite direction until such trip finger engages said projection to disengage the latter from said peripheral ratchet whereupon said tension spring angularly shifts said second drum and the ratchet thereof into engagement with another ratchet tooth, said face of said second eccentric having a peripheral projection for engaging the other of said termini in response to angular shifting of said pawl to place such termini in engagement with said periphery of said eccentric, and pawl means associated with each eccentric and with such shaft whereby said eccentrics can be rotated in a common direction opposite to that first mentioned for the actuation of the counting device.

10. In a counting device: a pair of coaxially mounted eccentrics; a first indicia drum mounted for angular movement coaxially with the first of said eccentrics; a second indicia drum mounted for angular movement coaxially relative to the second of such eccentrics, the latter having an internal ring gear secured thereto for rotation therewith; a spur gear rotatably journaled upon said first eccentric and having equi-spaced projection means thereon for engaging said internal ring gear, there being at least one less projection of said projection means than teeth of said internal ring gear; a ratchet secured to said second drum; pivotally mounted pawl means for engaging said spur gear and holding same against rotation during rotation of said first eccentric, said pawl means having a ratchet pin angularly shiftable therewith in pivotal motion and for engaging said ratchet; a tension spring linking said second eccentric and its indicia drum, whereby rotation of said first eccentric in one direction angularly shifts said second eccentric in an opposite direction thereby to tension said spring; and means rotatable with said first eccentric for disengaging said ratchet pin from said ratchet means thereby allowing said second drum to advance at least one ratchet tooth under the restoring action of said tension spring.

11. In a counting device, a pair of adjacent eccentrics having axes of rotation substantially perpendicular to a common plane; a first indicia means mounted for angular movement with a first of said eccentrics; a second indicia means mounted for angular motion relative to the second of said eccentrics; internal gear means and meshing planetary gear means operatively associating said first and second eccentrics, said gear means each having a different number of teeth, one of such gear means being journaled upon said first eccentric and the other of said means being secured to the second eccentric for rotation therewith; ratchet means coaxial with said second indicia means and secured thereto; pivotally mounted pawl means for holding that one of the aforementioned gear means against rotation which is journaled upon said first eccentric, ratchet pin means mounted for angularly shifting with such pawl means and for engaging said ratchet means; spring means for linking said second eccentric and said second indicia means, whereby rotation of said first eccentric in one direction angularly shifts said second eccentric in an opposite direction thereby to tension said spring; means rotatable with said first eccentric for momentarily disengaging said ratchet pin and ratchet means thereby causing said second indicia means to advance under the influence of said spring means and to be arrested by said pin and ratchet means.

12. In a counting device; a pair of adjacent eccentrics having axes of rotation substantially perpendicular to a common plane; a first indicia means mounted for angular movement with and coaxially of a first of said eccentrics; a second indicia means mounted coaxially of the second of said eccentrics and for angular motion relative thereto; an internal gear and meshing planetary gear operatively associating said first and second eccentrics, said gears having different numbers of teeth, one of such gears being journaled upon said first eccentric and the other of said gears being secured to the second eccentric for rotation therewith; ratchet means coaxial with said second indicia means and secured thereto; pivotally mounted pawl means for holding that gear against rotation which is journaled upon said first eccentric, ratchet pin means mounted for angularly shifting with such pawl means and for engaging said ratchet means; spring means for linking said second eccentric and said second indicia means, whereby rotation of said first eccentric in one direction angularly shifts said second eccentric in an opposite direction thereby to tension said spring; means rotatable with said first eccentric for momentarily disengaging said ratchet pin and ratchet means after a preselected angular shift of such first eccentric thereby causing said second indicia means to advance under the restoring action of said spring means and to be arrested by said pin and ratchet means; indicia reference means associated With said second eccentric and angularly shiftable therewith, and means operable in response to disengagement of said pawl means from such aforementioned gear means for movement into the path of such indicia reference means whereby all of said indicia means can be angularly shifted each to a preselected angular norm in response to rotation of said eccentrics in a common direction.

13. In a counting device: a pair of adjacent eccentrics having axes of rotation substantially perpendicular to a common plane; a first indicia means mounted for angular movement with and coaxially of a first of said eccentrics; a second indicia means mounted coaxially of the second of said eccentrics and for angular motion relative thereto; internal gear means and meshing planetary gear means operatively associating said first and second eccentrics, one of such gear means being journaled upon said first eccentric and the other of said gear means being secured to the second eccentric for rotation therewith; ratchet means coaxial with said second indicia means and secured thereto; pivotally mounted pawl means for holding that of the aforementioned gear means against rotation which is journaled upon said first eccentric, ratchet pin means mounted for angularly shifting with such pawl means and for engaging said ratchet means; spring means for linking said second eccentric and said second indicia means, whereby rotation of said first eccentric in one direction angularly shifts said second eccentric in an opposite direction thereby to tension said spring; means rotatable with said first eccentric for momentarily disengaging said ratchet pin and ratchet means thereby causing said second indicia means to advance under the influence of said spring means and to be arrested by said pin and ratchet means; indicia reference means associated with said second eccentric and angularly shiftable therewith, means operable in response to disengagement of said pawl means from such aforementioned gear means for movement into the path of such indicia reference means whereby all of said indicia means can be angularly shifted each to a preselected angular norm in response to rotation of said eccentrics in a common direction, a counter shaft for mounting said eccentrics and shiftable axially relative thereto; clutch means having a driving member for engaging a driven member secured to said first eccentric, one of said members being axially shiftable with said counter shaft to disengage said clutch means; detent means for holding said counter shaft in a preselected angular position; means for driving said eccentrics by said counter shaft in response to rotation of the latter in said common direction, and means for shifting said pawl means out of engagement with said gear means and into the path of said indicia reference means in response to disengagement of said detent means.

No references cited. 

